US10794274B2 - Gas turbine facility with supercritical fluid “CO2” recirculation - Google Patents
Gas turbine facility with supercritical fluid “CO2” recirculation Download PDFInfo
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- US10794274B2 US10794274B2 US15/391,427 US201615391427A US10794274B2 US 10794274 B2 US10794274 B2 US 10794274B2 US 201615391427 A US201615391427 A US 201615391427A US 10794274 B2 US10794274 B2 US 10794274B2
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- 239000012530 fluid Substances 0.000 title claims abstract description 39
- 239000007789 gas Substances 0.000 claims abstract description 129
- 239000000567 combustion gas Substances 0.000 claims abstract description 36
- 239000000446 fuel Substances 0.000 claims abstract description 33
- 239000007800 oxidant agent Substances 0.000 claims abstract description 24
- 230000001590 oxidative effect Effects 0.000 claims abstract description 24
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 20
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- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 60
- 229910002092 carbon dioxide Inorganic materials 0.000 description 30
- 239000001569 carbon dioxide Substances 0.000 description 30
- 239000001301 oxygen Substances 0.000 description 14
- 229910052760 oxygen Inorganic materials 0.000 description 14
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 13
- 239000007788 liquid Substances 0.000 description 9
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- 150000002430 hydrocarbons Chemical class 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
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- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- UBAZGMLMVVQSCD-UHFFFAOYSA-N carbon dioxide;molecular oxygen Chemical compound O=O.O=C=O UBAZGMLMVVQSCD-UHFFFAOYSA-N 0.000 description 1
- 229910002091 carbon monoxide Inorganic materials 0.000 description 1
- 230000008859 change Effects 0.000 description 1
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/34—Gas-turbine plants characterised by the use of combustion products as the working fluid with recycling of part of the working fluid, i.e. semi-closed cycles with combustion products in the closed part of the cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
- F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
- F02C1/08—Semi-closed cycles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
- F02C7/10—Heating air supply before combustion, e.g. by exhaust gases by means of regenerative heat-exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K19/00—Regenerating or otherwise treating steam exhausted from steam engine plant
- F01K19/10—Cooling exhaust steam other than by condenser; Rendering exhaust steam invisible
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
-
- Y02E20/322—
Definitions
- Embodiments described herein relate generally to a gas turbine facility.
- FIG. 3 is a system diagram of a conventional gas turbine facility in which a part of carbon dioxide generated in a combustor is circulated as working fluid.
- oxygen separated from an air separator (not illustrated) is regulated in flow rate by a flow rate regulating valve 310 and is supplied to a combustor 311 .
- Fuel is regulated in flow rate by a flow rate regulating valve 312 and is supplied to the combustor 311 .
- This fuel is, for example, hydrocarbon.
- the fuel and oxygen react (combust) in the combustor 311 .
- the flow rates of fuel and oxygen are regulated to be of a stoichiometric mixture ratio in a state that they are completely mixed.
- the combustion gas generated in the combustor 311 is introduced into a turbine 313 .
- the combustion gas which performed an expansion work in the turbine 313 passes through a heat exchanger 314 and then further through a heat exchanger 315 .
- the water vapor condenses into water.
- the water passes through a pipe 316 and is discharged to the outside.
- a generator 317 is coupled to the turbine 313 .
- Dry working gas (carbon dioxide) separated from water vapor is compressed by a compressor 318 .
- a part of the compressed carbon dioxide is regulated in flow rate by a flow rate regulating valve 319 and is exhausted to the outside.
- the rest of the carbon dioxide is heated in the heat exchanger 314 and is supplied to the combustor 311 .
- turbine load control is performed from a full speed no load (FSNL) to a rated value.
- FSNL full speed no load
- the pressure of the working fluid in this gas turbine facility is at high pressure, and thus the volumetric flow rate of the working fluid in the compressor 318 is small. Accordingly, as the compressor 318 , an axial compressor is not suitable, and a centrifugal compressor is used.
- a part of the carbon dioxide supplied to the combustor 311 is introduced into a combustion zone together with the fuel and oxygen.
- the rest of the carbon dioxide is used to cool wall surfaces of the combustor 311 and dilute the combustion gas.
- the carbon dioxide introduced into the combustor 311 is introduced into the turbine 313 together with the combustion gas.
- an amount of carbon dioxide equivalent to the amount of carbon dioxide generated by combusting fuel and oxygen in the combustor 311 is exhausted to the outside of the system.
- the carbon dioxide exhausted to the outside of the system is collected by, for example, a recovery apparatus. Further, for example, it is also possible to utilize the exhausted carbon dioxide for pushing out residual oil from an underground rock formation of an oil field. On the other hand, the carbon dioxide left in the system circulates through the system.
- flame formed in the combustor 311 is affected by, for example, a jetting velocity of carbon dioxide jetted into the combustor 311 (hereinafter referred to as a combustor jetting velocity V).
- V This combustor jetting velocity V is defined by following equation (1).
- V G ⁇ T ⁇ R ⁇ Z /( P ⁇ A ) (1)
- G is a volumetric flow rate of carbon dioxide flowing into the combustor 311
- T is a temperature of carbon dioxide flowing into the combustor 311
- R is a gas constant
- Z is a coefficient of compressibility.
- P is a pressure of carbon dioxide flowing into the combustor 311
- A is a total opening area of an opening passed through by carbon dioxide which flowed into the combustor 311 .
- the flame is affected by the combustor jetting velocity V. Accordingly, when the turbine load control is performed in the gas turbine facility, for example, it is preferred to control this combustor jetting velocity V in an appropriate range so as to achieve stabilization of the flame.
- FIG. 1 is a system diagram of a gas turbine facility of an embodiment.
- FIG. 2 is a diagram illustrating the relation between an inlet pressure of a turbine and a combustor jetting velocity V in each load state in the gas turbine facility of the embodiment.
- FIG. 3 is a system diagram of a conventional gas turbine facility in which a part of carbon dioxide generated in a combustor is circulated as working fluid.
- a gas turbine facility includes a combustor combusting fuel and oxidant, a turbine rotated by combustion gas exhausted from the combustor, a heat exchanger cooling the combustion gas exhausted from the turbine, and a water vapor remover removing water vapor from the combustion gas which passed through the heat exchanger to regenerate dry working gas therefrom.
- the gas turbine facility has a compressor compressing the dry working gas until it becomes supercritical fluid, a combustor introduction pipe guiding a part of the dry working gas of supercritical fluid exhausted from the compressor to the combustor via the heat exchanger, an exhaust pipe branched from the combustor introduction pipe on an upstream side of the heat exchanger to exhaust a part of the dry working gas flowing through the combustor introduction pipe to the outside, and a bypass pipe introducing a remaining part of the dry working gas of supercritical fluid exhausted from the compressor into a pipe coupling an outlet of the turbine and an inlet of the heat exchanger.
- FIG. 1 is a system diagram of a gas turbine facility 10 of an embodiment.
- the gas turbine facility 10 has a combustor 20 combusting fuel and oxidant.
- a pipe 35 supplying fuel to the combustor 20 is provided with a flow rate regulating valve 15 for regulating a flow rate of fuel.
- a pipe 36 supplying oxidant to the combustor 20 is provided with a flow rate regulating valve 16 for regulating a flow rate of oxidant. Note that the flow rate regulating valve 16 functions as an oxidant flow rate regulating valve.
- the fuel for example, hydrocarbon such as natural gas or methane, or coal gasification gas can also be used.
- oxygen is used as the oxidant. This oxygen is obtained by, for example, separating from the atmosphere by an air separating apparatus (not illustrated).
- the combustion gas exhausted from the combustor 20 is guided to a turbine 21 .
- This turbine 21 is rotated by combustion gas.
- a generator 22 is coupled to this turbine 21 .
- the combustion gas exhausted from the combustor 20 mentioned here contains combustion product, generated by combustion of fuel and oxidant, and dry working gas (carbon dioxide), which will be described later, supplied to the combustor 20 and exhausted together with the combustion product from the combustor 20 .
- the combustion gas exhausted from the turbine 21 is cooled by passing through a heat exchanger 23 interposed in a pipe 40 .
- the combustion gas which passed through the heat exchanger 23 further passes through a heat exchanger 24 interposed in the pipe 40 .
- a heat exchanger 24 By passing through the heat exchanger 24 , water vapor contained in the combustion gas is removed, and dry working gas is regenerated from the combustion gas.
- the heat exchanger 24 By passing through the heat exchanger 24 , the water vapor condenses into water. This water passes through a pipe 41 for example and is discharged to the outside.
- the heat exchanger 24 functions as a water vapor remover removing water vapor.
- the flow rates of fuel and oxygen supplied to the combustor 20 are regulated to be of a stoichiometric mixture ratio (equivalence ratio).
- the components of the dry working gas are mostly carbon dioxide. Note that the dry working gas also includes the case where, for example, a minute amount of carbon monoxide or the like is mixed in.
- the dry working gas is guided to a compressor 25 by the pipe 40 .
- the dry working gas is compressed by the compressor 25 until it becomes supercritical fluid.
- pressure of the dry working gas is, for example, 8 MPa to 9 MPa
- temperature of the dry working gas is, for example, 35 to 45° C.
- the supercritical fluid refers to a state under a temperature and a pressure equal to or higher than a critical point.
- the compressor 25 for example, a centrifugal compressor is used.
- the compressor 25 is, for example, coupled coaxially to the turbine 21 so as to prevent over-speeding of the turbine 21 .
- the compressor 25 rotates constantly at a rated rotation speed of the turbine 21 when the turbine 21 is at a rated value.
- the centrifugal compressor has a small surge margin with respect to increase in pressure ratio.
- the centrifugal compressor is preferred to be operated with a volumetric flow rate and a pressure ratio which are constant.
- the pressure at an inlet of the compressor 25 is also at a constant value.
- the pressure at an outlet of the turbine 21 is constant. This is preferred also in view of sealing characteristics of the turbine 21 and stable use of the heat exchangers 23 , 24 . Note that in order to maintain the pressure at the outlet of the compressor 25 constant, it is necessary to regulate a flow rate of dry working gas flowing through a pipe 45 , which will be described later.
- a part of the dry working gas of supercritical fluid exhausted from the compressor 25 passes through a pipe 42 and is guided to the combustor 20 .
- This pipe 42 functions as a combustor introduction pipe.
- a cooler 26 for cooling the dry working gas of supercritical fluid is interposed in the pipe 42 .
- the dry working gas of supercritical fluid maintains a pressure equal to or higher than the pressure of the critical point by passing through the cooler 26 , and is at a temperature lower than the temperature of the critical point.
- the dry working gas exits the state of supercritical fluid and becomes liquid.
- a pump 27 pressurizing the dry working gas which became liquid is interposed.
- the pump 27 pressurizes, for example, the dry working gas which became liquid according to a turbine load.
- the pump 27 is controlled in rotation speed by an inverter motor for example.
- the dry working gas which became liquid is pressurized by the pump 27 and also its temperature becomes equal to or higher than the temperature of the critical point.
- the dry working gas which became liquid passes through the pump 27 to thereby become the dry working gas of supercritical fluid again.
- rotation speed control is carried out by, for example, an inverter so as to make it pass setting points of the predetermined flow rate and pressure.
- the reason for making the dry working gas which passed through the cooler 26 become liquid while keeping a pressure equal to or higher than the pressure of the critical point is, for example, to prevent damage due to cavitation occurring when a two-layer flow of gas-liquid mixture enters the pump 27 under the condition that gas and liquid can exist together, such as a condition equal to or lower than the critical point. Further, by making it become liquid, condensation heat is not deprived, allowing operation while maintaining cycle efficiency.
- G t is a volumetric flow rate of the combustion gas at an inlet of the turbine 21
- T t is a temperature of the combustion gas at the inlet of the turbine 21
- P t is a pressure of the combustion gas at the inlet of the turbine 21 .
- a pipe 44 exhausting a part of the dry working gas flowing through the pipe 42 to the outside is branched from the pipe 42 between the pump 27 and the heat exchanger 23 .
- This pipe 44 functions as an exhaust pipe.
- the pipe 44 is provided with a flow rate regulating valve 29 for regulating the flow rate of the dry working gas to be exhausted. Note that the flow rate regulating valve 29 functions as an exhaust flow rate regulating valve.
- the dry working gas exhausted from the pipe 44 is collected by, for example, a recovery apparatus. Further, for example, it is also possible to utilize the exhausted dry working gas to push out residual oil from an underground rock formation of an oil field. For example, an amount of carbon dioxide equivalent to the amount of carbon dioxide generated by combusting fuel and oxygen in the combustor 20 is exhausted from the pipe 44 . Note that the dry working gas other than the dry working gas exhausted from the pipe 44 is guided to the combustor 20 and circulates through the system.
- the pipe 42 passes through the heat exchanger 23 and communicates with the combustor 20 .
- the dry working gas of supercritical fluid flowing through the pipe 42 obtains a heat quantity from the combustion gas exhausted from the turbine 21 and is heated thereby.
- the dry working gas passing through the pipe 42 and being introduced into the combustor 20 is, for example, jetted into a combustion zone together with the fuel and oxidant from the upstream side of the combustor 20 , or jetted into a downstream side of a combustion zone in a combustor liner from a dilution hole or the like after cooling the combustor liner.
- a jetting velocity to the combustor 20 of the dry working gas guided to the combustor 20 via the pipe 42 is preferred to be almost constant irrespective of the turbine load.
- the jetting velocity is the combustor jetting velocity V defined by the above-described equation (1).
- This combustor jetting velocity V is set so that a recirculation zone which contributes to flame stability is formed in an appropriate range of the combustion zone.
- the combustor jetting velocity V being almost constant refers to, for example, a range of ⁇ 10% with an average combustor jetting velocity in each turbine load as its center.
- the total opening area A of the opening passed through by dry working gas (carbon dioxide) which flowed into the combustor 20 is constant. Accordingly, when the combustor jetting velocity V is set almost constant irrespective of the turbine load, the mass flow rate of the dry working gas supplied to the combustor changes by the turbine load, but the volumetric flow rate becomes almost constant irrespective of the turbine load.
- the remaining part of the dry working gas of supercritical fluid exhausted from the compressor 25 passes through a pipe 45 and is introduced into the pipe 40 coupling the outlet of the turbine 21 and an inlet of the heat exchanger 23 .
- the pipe 45 functions as a bypass pipe.
- the pipe 45 is provided with a flow rate regulating valve 30 for regulating a flow rate of the dry working gas of supercritical fluid to be introduced into the pipe 40 .
- the flow rate of the dry working gas to be bypassed is regulated by the flow rate regulating valve 30 .
- the flow rate regulating valve 30 functions as a bypass flow rate regulating valve.
- the gas turbine facility 10 has a flow rate detecting unit 50 detecting the flow rate of fuel flowing through the pipe 35 , a flow rate detecting unit 51 detecting the flow rate of oxidant flowing through the pipe 36 , a flow rate detecting unit 52 detecting the flow rate of dry working gas flowing through the pipe 42 , a flow rate detecting unit 53 detecting the flow rate of dry working gas flowing through the pipe 44 , and a flow rate detecting unit 54 detecting the flow rate of dry working gas flowing through the pipe 45 .
- Each flow rate detecting unit is constituted of, for example, a flowmeter of venturi type, Coriolis type, or the like.
- the flow rate detecting unit 50 functions as a fuel flow rate detecting unit, the flow rate detecting unit 51 as an oxidant flow rate detecting unit, the flow rate detecting unit 52 as a combustor introduction flow rate detecting unit, the flow rate detecting unit 53 as an exhaust flow rate detecting unit, and the flow rate detecting unit 54 as a bypass flow rate detecting unit.
- the gas turbine facility 10 has a control unit 60 which controls openings of the respective flow rate regulating valves 16 , 29 , 30 based on detection signals from the respective flow rate detecting units 50 , 51 , 52 , 53 , 54 .
- This control unit 60 mainly has, for example, an arithmetic unit (CPU), a storage unit such as a read only memory (ROM) and a random access memory (RAM), an input/output unit, and so on.
- the CPU executes various types of arithmetic processing using, for example, programs, data, and the like stored in the storage unit.
- the input/output unit inputs an electrical signal from an outside device or outputs an electrical signal to an outside device.
- the input/output unit is connected to, for example, the respective flow rate detecting units 50 , 51 , 52 , 53 , 54 and the respective flow rate regulating valves 15 , 16 , 29 , 30 , and so on in a manner capable of inputting/outputting various signals.
- Processing executed by this control unit 60 is realized by, for example, a computer apparatus or the like.
- an output signal from the flow rate detecting unit 50 is inputted to the control unit 60 via the input/output unit. Based on the inputted output signal, the oxygen flow rate needed for making the equivalence ratio be 1 is calculated in the arithmetic unit by using programs, data, and so on stored in the storage unit. Note that the fuel flow rate is controlled by regulating an opening of the flow rate regulating valve 15 based on, for example, a required gas turbine output.
- control unit 60 Based on an output signal from the flow rate detecting unit 51 which is inputted from the input/output unit, the control unit 60 outputs an output signal for regulating the valve opening from the input/output unit to the flow rate regulating valve 16 so that the calculated carbon dioxide flow rate flows through the pipe 36 .
- the flow rate of dry working gas (carbon dioxide) of supercritical fluid introduced into the combustor 20 based on an output signal from the flow rate detecting unit 50 which is inputted from the input/output unit, the flow rate of dry working gas (carbon dioxide) of supercritical fluid introduced into the combustor 20 , the flow rate of the dry working gas of supercritical fluid exhausted from the pipe 44 , and the flow rate of the dry working gas of supercritical fluid bypassing via the pipe 45 are calculated. Note that calculations of these flow rates can be performed simultaneously as the above-described calculation of the oxygen flow rate. Further, the flow rate of the dry working gas can also be calculated based on an output signal from the flow rate detecting unit 51 .
- the flow rate of the dry working gas (carbon dioxide) introduced into the combustor 20 is calculated so that the combustor jetting velocity V becomes a set value.
- the flow rate of the dry working gas exhausted from the pipe 44 is, as described above, the amount equivalent to the amount of carbon dioxide generated by combusting fuel and oxygen in the combustor 20 .
- the flow rate of the dry working gas bypassed via the pipe 45 increases.
- the flow rate of the dry working gas bypassed via the pipe 45 decreases.
- the compressor 25 is coupled coaxially to the turbine 21 .
- the compressor 25 rotates constantly at a rated rotation speed of the turbine 21 .
- the pressure at the inlet of the compressor 25 is constant, and the pressure of the dry working gas at the outlet of the compressor 25 is a constant supercritical pressure.
- the flow rate of the dry working gas exhausted from the compressor 25 becomes constant.
- the control unit 60 outputs output signals for regulating the valve openings from the input/output unit to the flow rate regulating valves 29 , 30 so that the respective calculated flow rates of the dry working gas flow through the pipes 42 , 44 , 45 .
- those detected in the flow rate detecting unit 52 are flow rates of the dry working gas introduced into the combustor 20 and the dry working gas exhausted from the pipe 44 .
- the pump 27 is controlled by the control unit 60 to be at a rotation speed by which the flow rates of the dry working gas introduced into the combustor 20 and the dry working gas exhausted from the pipe 44 can be drawn in. Further, the pressure of the dry working gas at an outlet of the pump 27 is a pressure required at an inlet of the combustor 20 , in other words, the inlet of the turbine 21 .
- control unit 60 controls the flow rate regulating valve 30 for example.
- the combustor jetting velocity V can be maintained almost constant in the appropriate range.
- the recirculation zone is formed in the appropriate range of the combustion zone, and flame stabilization in the combustor 20 can be achieved.
- FIG. 2 is a diagram illustrating the relation between an inlet pressure of the turbine 21 and the combustor jetting velocity V in each load state in the gas turbine facility 10 of the embodiment.
- the outlet pressure of the turbine 21 in the illustration is 3 MPa.
- FSNL is a full speed no load state, and 25% indicates that the turbine load is 25%.
- the pressure of the dry working gas at the outlet of the compressor 25 is a constant supercritical pressure.
- the pump 27 is provided in the pipe 42 , and the pipe 45 bypassing a part of the dry working gas to the pipe 40 is provided. Even when the turbine load changes by them, they enable to maintain the combustor jetting velocity V substantially constant in the appropriate range and achieve flame stabilization in the combustor 20 .
- the combustor jetting velocity can be maintained in the appropriate range, and flame stabilization can be achieved.
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Drying Of Solid Materials (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
V=G×T×R×Z/(P×A) (1)
SWC=G t×(T t)1/2 /P t=constant equation (2)
Claims (13)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/391,427 US10794274B2 (en) | 2013-08-27 | 2016-12-27 | Gas turbine facility with supercritical fluid “CO2” recirculation |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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JP2013-175933 | 2013-08-27 | ||
JP2013175933A JP6250332B2 (en) | 2013-08-27 | 2013-08-27 | Gas turbine equipment |
US14/456,233 US9562473B2 (en) | 2013-08-27 | 2014-08-11 | Gas turbine facility |
US15/391,427 US10794274B2 (en) | 2013-08-27 | 2016-12-27 | Gas turbine facility with supercritical fluid “CO2” recirculation |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US14/456,233 Continuation US9562473B2 (en) | 2013-08-27 | 2014-08-11 | Gas turbine facility |
Publications (2)
Publication Number | Publication Date |
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US20170107904A1 US20170107904A1 (en) | 2017-04-20 |
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US10961920B2 (en) | 2018-10-02 | 2021-03-30 | 8 Rivers Capital, Llc | Control systems and methods suitable for use with power production systems and methods |
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US11686258B2 (en) | 2014-11-12 | 2023-06-27 | 8 Rivers Capital, Llc | Control systems and methods suitable for use with power production systems and methods |
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JP6636002B2 (en) * | 2017-11-22 | 2020-01-29 | 8 リバーズ キャピタル,エルエルシー | Gas turbine equipment |
WO2021079324A1 (en) | 2019-10-22 | 2021-04-29 | 8 Rivers Capital, Llc | Control schemes for thermal management of power production systems and methods |
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US9562473B2 (en) | 2017-02-07 |
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US20150059313A1 (en) | 2015-03-05 |
JP6250332B2 (en) | 2017-12-20 |
EP2853716B1 (en) | 2017-10-11 |
EP3273029B1 (en) | 2020-04-22 |
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